Multi-directional indexing apparatus

ABSTRACT

A multi-directional indexing apparatus for transporting articles in succession to and for depositing and/or picking-up such articles at a plurality of circumferentially disposed work stations. The apparatus comprises a multi-finger index table, with each finger having a vacuum pick-up head associated therewith for carrying the articles, and a drive mechanism including a barrel cam having a peculiarly shaped orbital cam passageway formed therein and a reciprocally movable cam follower for driving the barrel cam and the index table indirectly coupled thereto. A reciprocal, linear stroke of the cam follower during each composite indexing period sequentially effects, through the resultant rotational movements of the barrel cam, very precise multi-directional rotation and vertical displacement of the index table.

United States Patent Binkley MULTI-DIRECTIONAL INDEXING APPARATUS RalphN. Binkley, Yardley, Pa.

Western Electric Company, Incorporated, New York, N.Y.

Apr. 6, 1971 Inventor:

Assignee:

Filed:

Appl. No.:

US. Cl. 214/1 BH, 74/99 R, 214/1 BC Int. Cl. B66c l/02 Field of Search214/1 BH, 1 BC;

References Cited UNITED, STATES 'PATENTs 7/1968 Ligh 74/89 X FOREIGNPATENTS OR APPLICATIONS 9/1963 Great Britain 294/110 '8 PrimaryExaminerGerald M. Forlenza Assistant ExaminerGeorge F. AbrahamAtt0rneyW. M. Kain, R. P. Miller and A. C. Schwarz, Jr.

57 ABSTRACT A multi-directional indexing apparatus for transportingarticles in succession to and for depositing and/or picking-up sucharticles at a plurality of circumferentially disposed work stations. Theapparatus comprises a multi-finger index table, with each finger havinga vacuum pick-up head associated therewith for carrying the articles,and a drive mechanism including a barrel cam having a peculiarly shapedorbital cam passageway formed therein and a reciprocally movable camfollower for driving the barrel cam and the index table indirectlycoupled thereto. A reciprocal, linear stroke of the cam follower duringeach composite indexing. period sequentially effects, through theresultant rotational movements of the barrel cam, very precise multi- 23Claims, 16 Drawing Figures Patented Sept. 11, 1973 6 Sh89tBSheut 1ATTORNEY l l M In] TIP I06 HI Patented Sept. 11, 1973 6 Sheets-Sheet 2Patented Sept. 11, 1973- 6 Sheets-Sheet 3 Patented Sept. 11, 19733,757,963

\ 6 Shoots-Sheet 4 H l 55o so 1' i as H seq g 34 I l I 870 O l e3 j i 1W7 83 I! 56c 5 11 H I, ll w |/1 8 3 5% 21 9 F .1 i

Patentecl Sept. 11, 1973 3,757,963

I 6 Sheets-Sheet 5 PRFOT Q 5 F 5 M7 DIAPHRAGM FEED \y /5 32d IslARMATURE'\\ f 1 25c CYCLE I F1 o O.l 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 mm

| N D EX CYLINDER BARREL we CAM y I \N. Q o 6 INDEX TABLE '&

(ROTATION) I h 0 INDEX TABLE (VERTICAL AIR BURST (VACUUM OFF OVER-RIDE)Patented Sept. 11, 1973 6 Sheets-Sheet u MULTI-DIRECTIONAL INDEXINGAPPARATUS BACKGROUND OF THE INVENTION be precisely and sequentiallyimparted to an index table.

2. Description of the Prior Art In many manufacturing applications thereis a need for a rotary index table or turret which is capable of rapidlyand precisely indexing a plurality of circumferentially spaced work orarticle carrying fixtures thereon into alignment with one or morecircumferentially spaced and adjacent stationary work or test stationfixtures. Precise indexing is of utmost importance, of course, whensmall or miniaturized piece parts, articles, electrical components andthe like are involved, and especially where a physical work function isto be performed directly thereon such as drilling, forming, partinserting, bonding, etc.

The speed of indexing from one position to the next is likewise of greatimportance in many applications, especially where there are a number ofwork stations associated with a given rotary index table and/or wherethe work to be performed encompasses a period of time considerably lessthan the normal period required to index the table from one position tothe next. Work functions which often require but a fractional part of asecond may involve: electrically testing a component, perforating,forming or blanking an article, or staking,

. welding or bonding one article to another, to mention bearing on theefficiency of the work that can be performed on and the volume ofproduct which can be handled by a given indexing apparatus in a givenperiod of time.

Heretofore, most rotary indexing apparatuses have employed some form ofdirectly coupled drive mechanism, such as the well-known Ferguson drive,to provide intermittent indexing of the table from one position to thenext. The power source for such a drive is either intermittentlyoperated or continuously operated in conjunction with an intermittentlyoperated clutch mechanism. I

While such directly coupled drives provide adequate indexing of a tablein many applications, they have not proven to be a panacea for allapplications, especially where large numbers of inexpensiveand compactrotary indexing apparatuses are required for use in connection with highvolume manufacture of miniaturized articles.

More specifically, directly coupled, uni-directional drives are quiteexpensive, especially when they must satisfy demanding operatingrequirements, such as effecting relatively rapid and precise indexing ofrotary tables. Such drives are also generally quite heavy and bulky,even those designed for driving tables which are relatively small and oflight weight, and wherein no appreciable works forces are impartedthereagainst.

Another disadvantage of conventional, positive drive mechanisms is thatthey are not readily adaptable to multi-directional rotational movement.Such movement would be very desirable, for example, in aplications wherea large number of operating stations are employed. More specifically,through the use of oscillatory and partially overlapping indexing of arotary index table, only two article carrying fixtures would have to beprecisely aligned with an equal number of common stationary workfixtures, as distinguished from every article carrying fixture having tobe accurately aligned with every stationary work fixturecircumferentially spaced betweenthe load and unload'index positionsassociated with a given apparatus.

There is also a definite need for an indexing apparatus which not onlyis capable of imparting multidirectional movement to the table, but ofimparting periodic vertical displacement thereto in a sequential manner.Such compound movement would be of particular advantage with an indextable constructed in a multi-finger or spider configuration. Such atable, particularly with vacuum pick-up heads respectively secured tothe fingers thereof, would allow articles to be picked up from ordeposited on selectively aligned stationary work fixtures. Thereafter,the overlying article carrying fingers could be indexed to areasinterposed between different adjacent ones of a plurality of stationaryfixtures during each dwell period. This, of course, would allowretractable tooling disposed above the table to perform force-impartedwork directly on the articles, with the table itself bearing none of theforce. Concomitant advantages of this are that the indexing apparatuscould then be built with less stringent requirements relating to itssize, mass, structural rigidity, driving power and braking. All of thesefactors, of course, have'a direct bearing on the cost, simplicity andmaintenance requirements of a given indexing apparatus.

SUMMARY OF THE INVENTION An object of the present invention is toprovide a new and improved rotary indexing apparatus which obviates theneed for both complex and expensive directly coupled drive mechanisms.

Another object of the present invention is to provide a new and improvedindexing apparatus wherein multidirectional rotation is imparted to adriven index table thereof.

An additional object of the present invention'is to provide a new andimproved indexing apparatus wherein both multi-directional rotation andvertical displacement is sequentially imparted to a driven index tablethereof, and wherein the table is rapidly decelerated upon approachingeach index stop in such a manner as to obviate the need for an auxiliarybraking mechanism.

lt isstill a further object of the present invention to producesequentially both partially overlapping multidirectional rotation andvertical displacement ofa multi-finger index table having vacuum pick-upheads associated with each finger, and wherein each finger isrespectively restricted to sequential movement between and alignmentwith only three index positions associated with the table.

It is also an object of the present invention to provide a drivemechanism for rotary index tables which is light in weight, requires aminimum of space, is of simple and inexpensive construction, and whereinall of the main moving parts are readily accessible for routinemaintenance and/or replacement.

In accordance with the principles of the present invention, amulti-directional indexing apparatus is constructed to transportarticles in succession to a plurality of circumferentially disposed andrespectively aligned work stations. The apparatus, in one preferredillustrative embodiment, comprises a multi-finger index table, with eachfinger having a vacuum pick-up head associated therewith, a barrel camhaving a peculiarly shaped cam passageway (appearing oval-shaped in atwodimensional view) formed therein, and a reciprocally movable camfollower for driving the barrel cam and the index table indirectlycoupled thereto. A complete reciprocal stroke of the cam follower duringeach composite indexing period sequentially effects, through theresultant movements of the barrel cam, very precise multidirectionalrotation and vertical displacement of the index table.

In accordance with one illustrative embodiment, three successiverotational movements of the barrel cam of 45 clockwise, 90counterclockwise and 45 clockwise will, in turn, through an indirect,loss-motion coupling connection with the index table, produce threesuccessive rotational movements of the latter of 30 clockwise, 60counterclockwise and 30 clockwise.

By means of a spring-biased, cam-controlled mechanism, the table isvertically displaced downwardly whenever rotated to the two oppositeextreme angular positions. While in either of these positions, eachindex table finger overlies and is aligned with a different sta tionarywork fixture.

Such compound multi-rotational and verticalindex table movementadvantageously allows each vacuum pick-up head, for example, to beindexed 30 clockwise from a dwell position (whereat each finger isinterposed between a different pair of adjacent stationary fixtures) soas to pick up an article from an aligned stationary fixture and thentransfer it 60 counterclockwise to the other common and adjacentfixture, before being indexed 30 clockwise back to the dwell position.While the index table is in the dwell position, it becomes readilyapparent that work or machining operations may be performed on thearticles by tooling brought into contact therewith through the spacesdefined between adjacent fingers. In this way no work imparting force isexerted on the index table itself.

The use of the unique barrel cam as a multidirectional drive mechanismfor the index table also gives rise to the following advantages:minimizes the number of stationary and moving parts required, simplifiesand reduces the cost of construction, requires a minimum amount of spacebeneath the table and obviates the need for expensive and complexbraking mechanisms. Externally applied braking is' not required becauseof both an inherent decreasing rate of rotational deceleration impartedto the index table by the barrel cam while approaching each indexposition, and because of a shock-absorbing type of loss-motion couplingconnection between the barrel cam and index table. As a result, abruptor jarring stops and/or starts of the table are avoided. This becomes avery important factor when the article carrying fixtures on the tablecomprise vacuum pick-up heads. Such heads, of course, sometimes providethe orily effective means of rapidly picking-up, transferring andseating miniaturized articles, such as semi-conductor chips, thin filmcircuits, leads, terminals, eyelets, rivets, fasteners and the like.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a front elevational view ofa multidirectional indexing apparatus in accordance with a preferredembodiment of the invention;

FIG. 2 is a front sectional view illustrating the main structuralfeatures of the drive mechanism and camcontrolled support structure forthe multi-finger indexing table as embodied in accordance with theprinciples of the present invention;

FIG. 3 is a cross-sectional view of the drive mechanism taken along theline 3-3 of FIG. 2, illustrating in greater detail portions of thebarrel cam, support structure therefor and spring-biased structuralelements associated therewith;

FIG. 4 is a sectional side elevational view of a major portion of thedrive mechanism taken along the line 44 of FIG. 3;

FIG. 5 is a front elevational view primarily of the barrel cam portionof the drive mechanism taken along the line 5-5 of 'FIG. 4, andillustrating in greater detail the peculiar oval-shaped contour of thecam passageway formed therein and the position of the associated camfollower upon entering the passageway;-

FIG. 6 is a perspective view of a typical diaphragmarmature assembly ofa telephone receiver unit, the diaphragm initially being formed out ofsheet stock, then formed and perforated, and then an armature fed to andcrimped within a central aperture of the diaphragm, these operations alltaking place at different work stations associated with themulti-directional indexing apparatus of the present invention;

FIG. 7 is a front elevational view, partially in section, illustratingthe main structural features of the drive mechanism and cam-controlledsupport structure for the multi-finger index table as embodied inaccordance with the principles of the present invention, butdistinguishing primarily from FIG. 2 by the position of the barrel cam,cam follower and index table;

FIG. 8 is a front elevational view primarily of the bar rel cam portionof the drive mechanism as depicted in FIG. 5, but distinguishingtherefrom by depicting the associated cam follower at the point at whichit exits the passageway;

FIGS. 9A, 9B are partial, detail front elevational views, FIG. 9A takenalong the line 9A--9A of FIG. 2, illustrating two different angularpositions of the spring-biased cam controlled support member associatedwith the indexing table, and the manner by which vertical displacementof the table is effected through the utilization of loss-motion betweenthe barrel cam and the support member;

FIG. 10 is an enlarged plan view of the multi-finger indexing table, andfurther illustrates generally, in phantom, the stock feed and dischargestations and various work stations which are employed in oneillustrative application in assembling diaphragm-armature units fortelephone receivers of the type depicted in prises the non-dwell half ofa typical composite operating period, and

FIGS. 12A-I2D are partial, detail perspective views illustrating fourdifferent angular positions of the barrel cam and the associatedspring-mounted table support member coupled thereto relative to thereciprocally driven cam follower, the figures depicting the relativepositions of the aforementioned members at 0, 0.3, 0.7, and 1 secondintervals of a typical operating cycle as indicated in the timing chartof FIG. 10.

DETAILED DESCRIPTION In accordance with the principles of thepresent-ina multi-directional indexing apparatus, designated generallyby the reference numeral 20, is mounted on a stationary support table22. The apparatus includes a drive mechanism 23 supported by andpositioned beneath the stationary table 22. Mechanism 23 indirectlysupports and imparts selective multidirectional rotation to amulti-finger index table 25 (best seen in FIG. positioned above thestationary table 22. The index table is mounted on a cylindricalspring-biased index support member 30 which is indirectly coupled to thedrive mechanism.

A plurality of stationary work station support fixtures 32a-32f (seeFIG. 10) are secured to an auxiliary support base 34 which, in turn, issecured to the stationary table 22. These stationary workfixtures arecircumferentially spaced beneath and in close proximity to the undersideof the index table 25. A plurality of work operating heads 37, normallydisposed above the index table, are secured to a support plate 39 which,in turn, is mounted for slidable, reciprocal movement along four guiderods 41 positioned in space quadrature. As such, the operating heads maybe periodically brought into work engaging relationship with articlestransported by-the index table to the respectively aligned stationarywork fixtures 32. Vertical movement is imparted to the support plate 39,and thereby to the operating heads 37 (including tooling), through theactuation of a pneumatic cylinder 45, only partially shown in FIG. I,which has a piston 47 connected to the movable support plate.

As the particular work functions performed at the various work stationsare not of particular importance with respect to gaining anunderstanding of the novel features embodied in the present invention,they will only be briefly described hereinafter in connection with oneillustrative manufacturing operation wherein a diaphragm-armatureassembly 51 (FIG. 6), used in certain telephone receiver units, isformed and assembled.

Considering now in greater detail the multidirectional drive mechanismdesignated generally by the reference numeral 23 in FIG. 1, and bestseen in FIGS. 2-8, a cylindrical barrel cam 55 having a. peculiarlyshaped orbital passageway 56 formed therein is secured by a plurality ofsuitable fasteners 59 (FIGS. 2 and 7) to an outer rotatable supportsleeve 58. The orbital passageway 56 in a preferred embodiment comprisestwo mutually disposed arcuate sections 56a, 56b, with the correspondingends thereof forming upper and lower communicating vertices. As the wallportion 55a of the barrel cam, defined within the continuous orbitalpassageway, is in actuality positioned in free-space relation withrespect to the remainder of the barrel cam wall, the portion 55a issecured to a thin wall portion 58a of the support plate 58. (best seenin FIGS. 3 and 4). The

wall portion 58a also has a flat outer surface on which a support plate60 is secured by any suitable means.

The support sleeve 58 is mounted for rotational movement within an outercylindrical and stationary .a cylindrical shank 67. A lower flange 67bof the shank is secured to a mating flange 69 which, in turn, is securedto the outer housing of a pneumatic cylinder 71, preferably of thedouble acting type, illustrated in FIG. 1. The piston 73 of thepneumatic cylinder 71 is secured by a threaded member 75 (FIG. 2) to acylindrical drive rod 77. Both pneumatic cylinders 45 and 71, of course,are supplied with air or fluid in a controlled, sequential manner fromsources and associated programmed, valve-actuated apparatus ofconventional design. 7

The drive rod 77 has a cam follower 81 rotatably secured thereto nearits lower end and a cam follower 83 rotatably secured thereto near itsupper extremity, cam follower 83 being best seen in FIGS. 4, 5 and 12.The lower cam follower 81 is confined for linear, retractable verticalmovement along a passageway 85 formed in a stationary cylindrical member86. This member is axially disposed within the cylindrical shank 67 andis secured thereto by an outwardly projecting flange portion 86aabutting against an undercut shoulder formed in the lower flange portion67b of the shank. Rotational movement of the member 86 is prevented byone or more fastening members 86b (FIGS. 2 and 7) additionally securingmember 86 to the stationary shank 67.

As can be readily seen in FIG. 2, the upper end of the linear passageway85 formed in the stationary member 86 is positioned so as to be indirect alignment and to communicate with a lower vertical extension 560of the orbital passageway 56 formed in the barrel cam 55. As such,actuation of the pneumatic cylinder 71, so as to progressively extendthe piston 73 thereof to a maximum limit, causes the drive rod 77 tomove the lower cam follower 81 progressively upward along the linearpassageway 85 from an initial lower starting position, depicted in FIG.2, to an upper position (not shown) near the upper end of thepassageway. Simultaneously, thecam follower 83 moves upwardly along theright half portion 56a of the orbital passageway from the initialposition depicted in FIGS. 2 and 5 to the upper vertex of thepassageway, depicted in FIG. 12C.

In accordance with the particular contour of the passageway 56 formed inthe barrel cam in one preferred illustrative embodiment, movement of thecam follower 83 from the position depicted in FIG. 12A to theintermediate position depicted in FIG. 12B results in the barrel cam 55being rotated clockwise 45. Movement of the cam follower 83 from theintermediate position to the upper vertex of the passageway 56 (FIG.12C) results in the barrel cam 55 being rotated counterclockwise 45 orback to the initial angular position depicted in FIG. 12A.

Upon progressive retraction of the drive rod 77 from within the barrelcam 55, the cam follower 83 moves downwardly along the left half portion568 of the orbital passageway. Movement of the cam follower 83 from theposition depicted in FIG. 12C (upper vertex) to the intermediateposition depicted in FIG. 12D results in the barrel cam 55 being rotatedcounterclockwise 45. Thus, it is readily seen that the barrel cam isrotationally displaced 90 in being rotated from the angular positiondepicted in FIG. 128 to the position depicted in FIG. 12D. Continueddownward movement of the cam follower 83 from the intermediate positiondepicted in FIG. 12D to the position depicted in FIG. 12A completes anorbit about the orbital cam passageway 56 and results in the barrel cam55 being rotated again clockwise 45 back to its initial or neutralangular position. From the position depicted in FIG. 12A, the camfollower 83 moves downwardly until it reaches itslowermost dwellposition within the linear passageway section 56c.

Such peculiar multi-directional rotational displacement of the barrelcam 55 is employed to effect very precise rotational displacement of themulti-finger index table 25 in opposite directions successively and withdifferent predetermined degrees of rotation in accordance with theillustrative embodiment. As will become more readily apparenthereinafter, this unique index table movement does not coincide directlywith that of the barrel cam becuase of the utilization of an indirectcoupling which involves a predetermined amount of loss motion orovertravel therebetween.

Considering the barrel cam again in greater detail, a spring-loaded,pivotal lever 87 (best seen in FIGS. 2, 3, and 7) is rotatably securedat its upper end through a fastener 88 to the support plate 60. A lower,inwardly extending vane-shaped portion 870 of the lever .87 extendsthrough a cutout 60a in the support plate 60 and communicates with thelower vertex of the passageway 56. Each of two springs 8989, secured atone end to an intermediate section of the lever 87 and at the oppositeend to brackets on the support plate 60 (FIG. 3), normally maintains theportion 87a of the lever in the position depicted in FIGS. 2, 5 and 12A.The lever is employed to insure that the cam follower 83, while movingupwardly will be directed into the right half (56a) of the orbitalpassageway 56. Whenever the cam follower 83 moves downwardly through thelower vertex of the passageway 56, it initially contacts the vaneshapedportion 870 of the lever and thereafter pivots the lever to the right,overcoming the normal springbias in the opposite direction appliedthereagainst, such that the vane-shaped portion arrives at the positiondepicted in FIG. 8. After the cam follower 83 moves downwardly past thevane-shaped portion 87a of the lever, the lever is again spring-biasedpivotally back to its normal position depicted in FIGS. 2 and 5.

It is very important that the cam follower 83, upon arriving at theupper vertex of the passageway 56, always descends downwardly along theleft half portion 56b thereof. To insure that this happens, both acontinuous force and a momentary snap-action type of rotational forceare imparted to the barrel cam 55 in a counterclockwise direction, thelatter force occurring whenever the cam follower 83 passes through theupper vertex of the passageway 56.

The continuous and snap-action rotational forces are accomplished inaccordance with the principles of the present invention by utilizing (asbest seen in FIGS. 1 and 3) a combination of a spring-biased band 92,partially wrapped around the rotatable support sleeve 58, and amechanism comprised of a pivotal arm 106,

spring-biased lever 108 and a cam follower 111. Considered morespecifically, the continuous rotational force imparted to the barrel cam55 is produced by the band 92, preferably made of metal. The band isfastened at one end to the outer wall of and extends approximatelylaround the rotatable support sleeve 58, when in its neutral or dwellposition. A slot 96 .forrned in the outer stationary housing 61 allowsthe band to pass therethrough and then around a pulley 98 rotatablysecured to a bracket 99. The band is continuously placed underspring-biased tension by means of a coil spring 101, secured through abracket 102 to a leg 103 of the stationary table 22, seen only in FIG.1.

Considering now in greater detail the aforementioned apparatus (FIG. 3)for imparting a momentary snap-action type of rotation to the barrelcam, it is seen that the arm 106 is applied to the bracket 99 on whichthe pulley 98 is mounted. One end of the lever 108 is pivotally securedto an upper end region of the arm 106, and supports the cam follower 111at the opposite end. During the major portions of the initial clockwiseand subsequent counterclockwise rotations of 45 each imparted to thebarrel cam 55, the cam follower lll normally rides along the outersurface of the rotatable support sleeve 58.

However, whenever the barrel cam approaches the neutral position movingin a counterclockwise direction, i.e., from the position depicted inFIG. 128 to that depicted in FIG. 12C, so as to position the camfollower at the upper vertex of the passageway 56, the cam follower 111is spring-biased against a tapered surface 113a of an undercut groove113 formed in and extending a short distance longitudinally around therotatable support sleeve 58 (best seen in FIGS. 3 and 4). Each time suchcam follower-tapered surface contact occurs, a momentarycounterclockwise rotational force is imparted to the barrel cam 55. Acoil spring 116, interposed between the lever 108 and a bracket 118affixed to the upper end of the pivotal arm 106, continuously biases thecam follower 111 in an off-center manner against the support sleeve 58.Opposite ends of the spring are seated within respectively alignedrecesses of the lever and bracket.

Thus, it is the spring-biased cam follower 1 l 1 and the spring-biasedband 92, in combination, that imparts the advantageous supplementarycounterclockwise rotational force against the barrel cam 55 whenever thecam follower 83 moves through the upper vertex of the passageway 56 intothe'left half portion 56b thereof.

During rotation of the barrel cam from the position depicted in FIG. 12Cback to the position depicted in FIG. 12A, the cam follower rides alongthe base of the groove 113 until just before the neutral position isreached. At that point the cam follower 111 is again in contact with thetapered cam surface 113a. However, as the cam follower 83 is forcefullybeing driven only downwardly at that time into the linear portion 560 ofthe passageway 56, the small, supplemental counterclockwise rotationalforces exerted on the support sleeve by the cam follower 111 and steelband 92 have no effect on the direction of movement of the cam follower83.

Attention will now be directed more specifically to the unique manner inwhich the multi-finger index table 25 is indirectly coupled to thebarrel cam 55 so as to produce compound rotational and verticaldisplacement thereof in a sequential manner. As previously noted, theindex table 25 may be either secured to or formed as an integral part ofthe rotatable support member 30. This support member, as best seen inFIGS. 2, 7, 9 and 12, is coaxially positioned on and supported by arotatable drive shaft 126 so as to be movable not only rotationally butaxially relative to the latter.

The drive shaft 126 is secured by any suitable means at its lower end tothe upper surface of the rotatable support sleeve 58. A helical spring131, coaxially positioned about the drive shaft 126, is partially seatedat its upper end within a cylindrical groove 133 of the supportmember-30, with the lower end of the spring being biased against theupper surface of a washer 128. Mounted in this manner, it is readilyapparent that any downward force exerted on the index table supportmember 30 will not only further compress the spring,

but result in the table being moved downwardly toward the washer 128,with the maximum possible vertical displacement being when the supportmember 30 abuts against the washer.

Controlled vertical displacement of the index table 25 (and of thesupport member 30) while positioned at predetermined angular positionsis accomplished through the use of a mutually disposed pair of biasingcam followers 135-135. These cam followers are rotatably secured toopposite ends of a support member 137 (best seen in FIGS. 2, 7, 9 and12), with the latter being rigidly secured to the upper end of therotatable drive shaft 126 by any suitable means, such as a threadedfastener 139 (FIG. 2). The helical spring 131 provides the means wherebythe cam followers 135135 are continuously maintained in spring-biascontact with and normally positioned at the vertices of respectivelyassociated V-shaped notches 141-141 formed in the upper edge of thesupport member 30.

As will become more apparent hereinafter in connection with adescription of the manner in which the index table is rotated,verticaldisplacement of the table is produced whenever the supportmember 30 is momentarily held stationary while the drive shaft 126forces the cam followers 135135, indirectly secured thereto, at leastpartially out of the V-notches 141 along the tapered surfaces 141athereof. The particular location of the mutually disposed V-notches 141is thus seen to be determinative of when the index table 25 isperiodically vertically displaced during each operating c cle.

As previously mentioned, in the illustrative application it is desiredthat the multi-fingerindex table25 not only be angularly displaced firstin one direction and then in the other, but in successively oppositedirections by different degrees of angular displacement, followed byrotation in a direction opposite to the second by an amount so as toarrive back at the initial position. While the orbital passageway 56 inthe barrel cam could be initially formed so as to provide the exactdegree of rotation desired during each successive. indexing period, itbecomes readily apparent that it would be quite difficult and expensiveto machine such a passageway in a barrel type cam with the accuracynormally required to satisfy precise indexing of the table in demandingmanufacturing applications. I

Moreover, if the index table were directly coupled to and driven by thebarrel cam, with the limits of angular displacement of the table therebybeing controlled solely by the particular configuration of the barrelcam passageway itself, it would be necessary to disassemble the entiredrive mechanism and incorporate a new barrel cam in the apparatus eachtime a change in index table rotational and/or vertical displacement wasde sired. If, on the other hand, a degree of loss motion or overtravelwere incorporated in the coupling of the index table to the barrel cam,then only that portion of the apparatus controlling loss motion orovertravel would have to be interchanged in order to alter the degree ofangular displacement of the table.

In accordance with the principles of the present invention, a form ofloss motion or overtravel is incorporated in the indexing apparatusembodied herein in a simple and readily interchangeable manner. Thesignificance of such loss motion and the manner in which it isaccomplished is best seen from a description of the actual angulardisplacements imparted to the index tablerelative to the barrel cam 55.For the aforementioned illustrative application of assembling adiaphragm-armature assembly of the type depicted in FIG. 6, it wasdesired to rotate the index table 30 clockwise, then counterclockwise,then 30 clockwise (see FIG. 10). v i

To accomplish the initial index table displacement of 30 clockwise, thebarrel cam 55, as well as the drive shaft 126 secured thereto, isrotated 45 as a result of the cam follower 83 moving from the positiondepicted in FIG. 12A to, the position depicted in FIG. 128. As such, 15of loss motion is required in order to restrict the rotational movementof the index table to 30. This degree of loss motion is accomplished byforming a longitudinally extending cam slot 145 along a portion of thewall of the index table support member 30 (best seen in FIGS. 9 and12D). A cam follower 146, which is rotatably secured to a shaft147, ispositioned to communicate with the slot 145. The shaft is supported atone end to a bracket 149 (FIGS. 1, 2 and 7) which, in turn, is securedto the auxiliary support plate 34.

I As can be best seen in FIGS. 9A and 93, upon both the drive shaft 126and the index table support member 30 being rotated 30, the cam follower146 moves into contact with a vertical sidewall 145a of the slot145(FIG. 98). At that point, the support member 30 is prevented fromrotating the additional 15 with the drive shaft 126, because the shaft147 supporting the cam follower 146 is secured to the stationary bracket149. As a result, the cam followers -135 start to ride out of theV-notches 141 formed in the upper edge of the index table support member30, thereby causing the latter to be vertically displaced. As the indextable 25 is formed either as an integral part of. or otherwise securedto the support member 30, it likewise is vertically displaced. In theillustrativeembodiment, such vertical displacement is three-eighthsinch.

Again with reference to FIG. 98, it is seen that the elongated cam slot145 formed in the table support member 30 has a somewhat curved camsurface base which merges into rounded corners which, in turn, mergeinto respectively adjacent vertical sidewalls 145a, l45b. Thisparticular cam slot configuration results in the cam follower 146contacting the base of the slot only along the end regions thereof. Assuch, the cam follower 146, in approaching agiven lower corner of theslot 145, gently urges the index table support member 30 downwardly.just before the cam follower arrives at and contacts the particularsidewall associated with that corner. In this way, the cam follower 146effectively initiates both the vertical displacement of the index tableand the movement of the cam followers 135--135 out of the vertices ofthe V-notches 141. This occurs immediately before the cam followers135-135 would otherwise be more abruptly driven from the vertices of thenotches by the positive rotation of the directly connected drive shaft126.

Upon the barrel cam 55 and drive shaft 126 being rotated 90counterclockwise from the position depicted in FIG. 128 to the positiondepicted in FIG. 12D, the support member 30 and index table 25 arerotated only 60 counterclockwise, thus, necessitating 30 of loss motionbetween the barrel cam-drive shaft combination and the supportmember-index table combination. This degree of loss motion is porducedin the following manner. During the first 15 of counterclockwiserotation of the barrel cam 55 and drive shaft 126, the spring-biasedforce exerted by the cam followers 135--l35 against the then contactingtapered surfaces of the V-notches 141 results in the support member 30and index table remaining stationary with respect to rotation, butrising vertically to the previous elevation thereof. The period of timeduring whichthe initial 15 of loss motion occurs between the barrel cam55 and the index table 25, and the magnitudes of the relative movementsthat occur there-between during that period are best illustrated in thetiming chart depicted in FIG. 11. I

Only after the cam followers 135-435 reach the vertices of therespective V-notches 141 will the support member and index table 25begin to rotate counter clockwise with the barrel cam 55. When thishappens, of course, the relative movement between the support member 30and the fixed position of the cam follower 146, results in the latterbeing brought into contact with the left sidewall 14511 of the cam slot.It is this relative movement between the cam follower 146 and thesupport member 30 that encompasses 60 of counterclockwise rotation ofthe table support member 30 and index table 25. At that time, the camfollower 146 again acts as a positive table stop while'the barrel cam 55and drive shaft 126 continue to rotate the final 15 of the total of 90of rotation in a counterclockwise direction. This last 15 of rotationalmovement again causes the cam followers l135 to move at least partiallyout of the V-notches 141 and, thereby, vertically displace the supportmember 30 and index table The subsequent and final clockwise rotation ofthe barrel cam 45 during a given indexing period, from the positiondepicted in FIG. 12D to the position depicted in FIG. 12A, results inthe support member 30 and the index table 25 moving clockwise only 30before arriving at the original or dwell position. Again, because of thespring-biasedforce exerted by the cam followers l35- 135 against thethen-contacting cam surfaces of the V-notches 141, the support member 30and index table 25 do not rotate during the first 15 out of the total of45 of final clockwise rotational movement of the barrel cam 55 and driveshaft 126 back to the original or dwell position.

It becomes readily apparent, of course, that by simply varying thelocation and number of V-notches 141 formed in the upper edge of thesupport member 30, any number of vertical displacements may be impartedto the index table 25. It should also be understood that the notches 141need not be of V-shaped configuration, but rather, could comprise anyone of a number of straight line or curved configurations to satisfy notonly the degree of vertical displacement desired, but the speed andduration of such displacement.

Similarly, it should be readily appreciated that the orbital passageway56 may take any one of a number of other forms. For example, one portionor section thereof need not even be arcuate or otherwise nonlinear alongits length. More specifically, for certain applications, it may bedesirable to have only one portion or section of a continuous, orbitalpassageway nonlinear, with the remainder being linear, such as in thecapital letter D. As a matter of fact, the passageway in certain limitedapplications need not even be orbital, but rather, simply double endedwith an arcuate or non-linear section along the length thereof. What isrequired in accordance with the principles of the present invention isthat the passageway 56 have a non-linear or arcuate section so that therectilinear path of travel of the cam follower 83 will force the barrelcam to rotate to an angular position whereby every point'along thepassageway will be brought into alignment with the cam follower as itpasses therethrough. It thus can be seen that the magnitude ofrotational displacement of the barrel cam and the direction thereof,will be dependent upon both the degree of longitudinal displacement andthe angle of inclination of the particular passageway at any pointtherealong relative to the rectilinear path of travel of the camfollower 83, as measured from an arbitrary neutral or dwell position ofthe barrel cam 55.

For the particular illustrative manufacturing application describedherein, each of the index table fingers 25a-25e supports a vacuumpick-up head designated generally by the reference numerals 15la151e,best seen in FIGS. 2, 7 and 10. Each of these heads is respectivelyconnected by a separate vacuum line 154a-154e to a common cylindricalvacuum line 157 which, in turn, is connected through a supply line 161to a suitable selectively actuated vacuum pump 163 (shown onlysymbolically in FIG. 10).

With such vacuum pick-up heads, it is seen that periodic compoundrotational and vertical displacement of the index table 25 will allow aparticular article to either be placed on the upper surface of a givenstationary fixture 32 in alignment therewith, or picked up therefrom forsubsequent transfer to the next succeeding stationary fixture.

With the various structural details of the multidirectional indexingapparatus having been described in detail hereinabove, a typicalsequence of indexing periods of the apparatus will now be described inconnection with the illustrative manufacturing application whereindiaphragm-armature units 51 of the type depicted in FIG. 6 areassembled. To this end, attention will be directed primarily to the planview of the index table 25- in FIG. 10, the timing chart in FIG. 11, andthe series of perspective views of the drive mechanism depicted in FIG.12.

As the actual operations performed on the parts at the various workstations, the nature of the tooling therefor and the manner by which thetooling is operated are all only incidental to the present invention,reference to the various work station operations will only be in generalterms and for the sole purpose of better understanding the uniquefeatures and mode of operation of the multi-directional indexingapparatus.

To this end, and by way of preliminary background information of generalinterest only, the diaphragm 51a is initially formed out of thin sheetstock material, such as aluminum, into a circular, concave configurationhaving a central aperture in which a circular, preformed armature 51b,such as of 2 percent vanadium permendur, is retained. The assembly ofthese two parts, as it relates to the use of the present indexingapparatus, involves the following successive operations respectivelyperformed at different work stations: blanking the diaphragm out ofsheet stock; drawing or forming the diaphragm into a slightly concavecylindrical configuration; perforatingthe diaphragm to form a centralaperture therein, and finally crimping a preformed armature within theaperture of the diaphragm to form a completely assembleddiaphragm-armature unit. These operations, of course, require precisefeeding, seating, picking-up and transferring of the parts in asequential manner during each complete operating cycle.

Considered now more specifically in relation to the mode of operation ofthe indexing apparatus, during the first dwell period of an initialoperating cycle, with the index table fingers 25ae in a dwell position,as depicted in FIG. 10, an operating head 37 including a punch 37a,depicted only generally in FIG. 1, is brought down into engagement withsheet stock material 165, fed by suitable means (not shown) to andsupported on the stationary fixture mm in alignment with the punch. Thepunch initially blanks out a diaphragm 51a having the desired outsidedimensions.

It will suffice to simply say at this point that retractable verticalmovement of the punch 37a, as well as of the other tooling, supported onthe vertically retractable plate 39, may be effected in a programmedmanner under the control, for example, of the pneumatic cylinder d5mounted on the support plate or shoe 46 disclosed in FIG. 1. It shouldbe understood, of course, that not only simultaneous but selectivecontrol of the vertical movements of the various tooling (as well as ofany driving power therefor, when necessary for a particularapplication), may be accomplished with any one of a number ofconventional mechanisms and machining control systems.

In accordance with the particular operating cycle times employed for theillustrative application described herein, the blanking operation isaccomplished during the dwell period which encompasses slightly morethan'l second in duration. Immediately after that period of time, thebarrel cam 55 is rotated 45 clockwise whereas the index table 25,because of the previously described loss motion or overtravel built intothe drive mechanism, rotates only 30 clockwise.

Upon the barrel cam 55 rotating clockwise the first 30 of the total 45during the initial composite indexing period, the cam followers 135-135,normally positioned within the V-notches 141 in the upper edge of theindex table support member 30, are moved at least partially out of thenotches because of the overtravel of the drive shaft 126 relative to theindex table support member 30 as previously described. This results in amomentary downward vertical displacement of the index table 25 ofthree-eighths inch which is sufficient to allow each vacuum pick-up headassociated with a different index finger to make contact with and pickup an article nested in an aligned stationary work fixture 32.

With particular reference to FIG. 10, the article initially picked up bythe vacuum head of index finger 25a, for example, is the previouslyblanked out diaphragm 510 which, at that point, simply comprises a flat,circular blank. This initial down and up vertical displacement of theindex table 25 takes place over a time period of approximately 0.2 of asecond, as best seen from the timing graph designated Index TableVertical Displacement."

Before such vertical displacement of the index table 25 is completedhowever, which occurs after 0.4 seconds of a composite indexing period,the barrel cam 55, in response to the upward movement of the camfollower 83, has already started to rotate counterclockwise 90.

It should be appreciated that while the drive rod 77 is moving eitherinto or out of the barrel cam 55, the latter is likewise continuouslymoving either clockwise or counterclockwise, and only stops when thedrive rod 77 is in the approximately I second dwell position depictedin'FIGS. 2 and 5. As for the index table 25, the timing graph relatingthereto discloses that it remains stationary with respect to rotationnot only during the 1 second dwell period, but during each verticaldisplacement period encompassing 0.2 of a second.

Upon the index table 25 being rotated 60 counterclockwise (in responseto the barrel cam 55 rotating 90 counterclockwise), it is seen from anexamination of FIG. 10 that the index finger 25a, for example,transports the previously blanked out diaphragm, indicated in phantom onstationary fixture 32a, to an overlying and aligned position with thestationary fixture 32b associated with the work station designated FormDiaphragm Contour. While in this angular position, the index table 25 isagain vertically displaced downwardly three-eighths inch while thevacuum is effectively cut off, such as by an overriding supply of airmomentarily applied to the vacuum lines 154 from a conventional source163, shown only symbolically in FIG. 10. As a result, the blanked outdiaphragm carried by the vacuum head 151 associated with index finger25a is released and nested on the upper surface of the alignedstationary work fixture 132b. The short period of time during which airissupplied to the vacuum heads is best seen by the graph designated AirBurst (vacuum override) depicted in FIG. 11. I

Immediately upon the index table 25 reaching the maximum downwardvertical displacement at this point in time, the barrel cam 55 starts torotate clockwise 45 and, after an initial 15 of overtravel, again drivesthe index table 25 with it 30 clockwiseto the original or dwell positiondepicted in FIG. 10. While in the dwell position, which as previouslymentioned encompasses slightly more than I second in duration, a drawingor forming operation is performed on the previously blanked outdiaphragm 51a, which is then seated on stationary fixture 13%. This isaccomplished, for example, by the upper surface of fixture 132b eithersupporting a die insert or having a desired contour tomate with aretractable die 137b, depicted generally in FIG. 1.

During the second composite indexing period, index table 25 is againrotated 30 clockwise and then vertirotated 60 counterclockwise and thenvertically displaced downwardly so that the diaphragm can be seated onthe stationary fixture 32c associated with the third work station. Inthe illustrative manufacturing application described herein, the thirdwork station actually comprises an idle station with no specific workbeing performed on the diaphragm.

The third composite indexing period results in the vacuum pick-up head151 associated with the index finger 250, for example, being rotated 30clockwise and then vertically displaced to pick up the aligneddiaphragm, then seated on the stationary fixture 32c, and transfer it 60counterclockwise to and seat it on the stationary fixture 32d associatedwith the fourth perforate diaphragm work station. With the index tablethen indexed 30 clockwise so as to again be in the dwell positiondepicted in FIG. 10, a perforating operation is performed on thediaphragm 510 by a punch 37d depicted only generally in FIG. 1.

While in this dwell position, a pre-formed cylindrical armature 51b,shown only in phantom in FIG. 10, is preferably fed in an automatedmanner along a feed track 171 to a position immediately beneath thevacuum pick-up head 151 associated with the index finger 25d. This maybe readily accomplished, for example, through the use of a vibratoryarmature supply bowl (not shown) in conjunction with the feed track 171.The terminating end of the feed track may, for example, not only bealigned with the vacuum pick-up head, but periodically pivotally raisedduring each dwell period so as to accurately and reliably position anarmature 51b in contacting relationship with the pick-up heads.

Accordingly, during the fourth indexing period under considerationherein, the vacuum pick-up head associated with the index table finger25d, for example, is rotated 30 clockwise with an armature 51b heldthereby and then vertically displaced to pick-up the perforateddiaphragm, then seated on the stationary fixture 32d. Both the diaphragmand the armature nested'thereon are then transferred 60 counterclockwiseto and seated on the stationary fixture 32:? associated with the fifthCrimp Diaphragm station. Thereafter, the index table is again indexed 30clockwise back to the dwell position.

During this latter dwell period the pre-formed cylindrical armature 51bis permanently secured to the diaphragm by a crimping operation. Thismay be readily accomplished by the stationary work fixture l32e havingan upper die surface that cooperates with a suitable retractablecrimping tool 137e, depicted only generally in FIG. 1. Such tooling maybe employed not only to permanently crimp the armature to the diaphragm,but to also provide a desired flange about the outer periphery of thediaphragm.

During the fifth composite indexing period, the same 7 sequence ofrotational and vertical displacements of the index table as previouslydescribed results in the vacuum pick-up head 151 associated with theindex finger 25a, for example, picking up and transferring thecompletely assembled diaphragm-armature unit 51 counterclockwise to anunload position overlying the discharge chute 167, which positionactually constitutes the sixth possible work station. Upon receipt of amomentary overriding air blast from the supply source 163, the assembledunit is released into the chute, with the index table thereafter beingrotated again clockwise 30 to the dwell position.

It is thus seen with reference to FIG. 10, that five composite indexingperiods, each comprising a multidirectional sequence of clockwise,counterclockwise and clockwise rotational displacements, interspersedwith two vertical displacements, comprises a complete operating cycle.More specifically, such a cycle results in a blanked outdiaphragm beingtransferred from a first work station, whereat it is depicted in phantomon stationary fixture 32a, to each of the four other circumferentiallyspaced work stations respectively associated with stationary workfixtures 32b'-e, before being discharged into the chute 167 located atthe last or sixth work station associated with the index apparatus.While reference was made hereinabove to the particular compoundrotational and vertical movements of only one specific index tablefinger at a time in describing each of the five successive indexingperiods, it should be readily appreciated, of course, that all of theindex fingers move simultaneously, as they form an integral part of theindex table.

In summary, a unique multi-directional indexing apparatus has beendescribed herein which advantageously produces compound rotational andvertical displacement of an index table in a sequential manner, allowswork or machining functions to be performed on piece parts withoutexerting any force on the table itself, and obviates the need forexpensive, bulky and uni-directional gear or cam driven mechanismsemployed heretofore. The drive mechanism also affords a simple means,through the principle of loss motion or overtravel, to vary the degreeof rotational displacement of the index table in opposite directions.Finally, the spring-biased and cam-controlled manner in which themulti-finger index table is mounted allows for precise and readilyadjustable control over the degree of and angular positions at which anynumber of vertical displacements may be imparted to the index table.

What is claimed is:

l. A multi-directional indexing drive mechanism for use with a rotaryindexing table, comprising:

rotatable drive means including at least one cylindrical member having acontinuous orbital cam passageway formed in the wall thereof andoriented generally in the axial direction of said cylindrical member,said cam passageway having a first section which is non-linear along atleast a portion of its length, and having a second section which mergesat opposite ends with said first section to form a continuous orbitalpassageway with upper and lower communicating vertices; and

reciprocal drive means at least partially extending within and movablerelative to said cylindrical member of said rotatable drive means, saidreciprocal'drive means having a rotatable cam follower secured theretoand communicating with said cam passageway, said cam follower duringeach indexing period being reciprocally movable along said passageway,with movement confined along a rectilinear path so as to rotate at leastsaid cylindrical cam member whenever the cam follower communicates withsaid non-linear section of said passageway, the particular direction andmagnitude of rotation imparted to said cylindrical cam member beingdependent upon both the degree of longitudinal displacement and theangle of inclination of said non-linear section of the passageway at anypoint therealong relative to the rectilinear path of travel of said camfollower, as measured from an arbitrary neutral position of saidcylindrical cam drive means, moves upwardly along the other sectionthereof, said lever being spring-biased to an open position by said camfollower whenever the latter makes contact therewith in movingdownmember, and wherein said cam follower, in moving wardly along theinitially closed section of said pasthrough successive complete orbitsin said orbital sageway. cam passageway, causes said cylindrical cammem- 5. A multi-directional indexing drive mechanism in ber to berotated in opposite directions out of, and accordance with claim 2further comprising: back into, its arbitrary neutral position on eachaspring-biased rotatable index table support member orbit in the samepredetermined sequence. coupled to said rotatable drive means, and 2. Amulti-directional indexing drive mechanism for vertical displacementmeans secured to said rotatable use with a rotary index table,comprising: drive means and cooperating with said support rotatabledrive means including a cylindrical member member to periodicallyvertically displace the lasthaving a cam passageway formed in the wallmentioned member a predetermined distance upon thereof, said passagewayhaving a first section being rotated to specific angular positionsduring which is arcuate along at least a portion of the each indexingperiod. length thereof, said first portion being oriented 6. Amulti-directional indexing drive mechanism in generally in the axialdirection of said cylindrical accordance with claim 5 furthercomprising: member, and a second section merging at opposite stop meanscoupled to said rotatable support memends and at oppositely inclinedangles with the corber allowing a predetermined degree of periodicresponding ends of said first section so as to form overtravel of saidrotatable drive means relative to a continuous orbital passageway withupper and said support member during each indexing period, lowercommunicating vertices, and said periodic overtravel allowing therotatable supreciprocal drive means at least partially extending portmember to be selectively displaced by differwithin and movable axiallyrelative to said cylindrient angular degrees of rotation than saidrotatable cal cam member, said reciprocal drive means havdrive meansduring each indexing period. ing a rotatable cam follower securedthereto and 7. A multi-directional indexing drive mechanism incommunicating with said cam passageway, said accordance with claim 3further comprising: cam follower during each indexing period beingaspring-biased rotatable index table support member rectilinearlymovable at least'from a first position coupled to said rotatable drivemeans,

I coinciding with the lower vertex of said passageway verticaldisplacement means secured to said rotatable to a second positioncoinciding with said upper verdrive means and cooperating with saidsupport tex of said passageway and then back to said first member toperiodically vertically displace the supposition, said rectilinearmovement of said cam folport member a predetermined distance upon beinglower during each indexing period resulting in at rotated to specificangular positions during each least said cylindrical cam member beingrotated at indexing period, and least once in opposite directions, theparticular distop means coupled to said rotatable support memrection andmagnitude 'of rotation imparted to said ber allowing a predetermineddegree of periodic cylindrical cam member being dependent uponovertravel of said rotatable drive means relative to both the degree oflongitudinal displacement and 40 said rotatable support member duringeach indexthe angle of inclination of said orbital passageway ingperiod, said periodic overtravel allowing the at any point 'therealongrelative to the rectilinear support member to be selectively stopped atdifferpath of travel of said cam follower, as measured ent predeterminedangular positions relative to said from an arbitrary neutral position ofsaid cylindrirotatable drive means, and with the rotation of said calcam member. 4 support member and the vertical displacement 3. Amulti-directional indexing drive mechanism in thereof being produced ina sequential manner by accordance with claim 2 further comprising: saidrotatable and reciprocal drive means.

a third linear passageway communicating with said 8. A multi-directionalindexing drive mechanism in lower vertex of said orbital passageway anddefinso accordance with claim 4 further comprising: ing whenever saidcam follower is confined therein a spring-biased rotatable index tablesupport member a neutral position and a dwell period of saidrotatcoupled to said rotatable drive means, able drive means, andwherein said cylindrical vertical displacement means secured to saidrotatable member comprises a barrel cam, wherein said redrive means andcooperating with said support ciprocal drive means includes acylindrical drive member to periodically vertically displace the suprod,wherein said second section of said passageport member a predetermineddistance upon being way includes an arcuate portion, and wherein saidrotated to specific angular positions during each cam follower in movingfrom said lower vertex of indexing period, and said orbital passagewayto the upper vertex thereof stop means coupled to said rotatable supportmemand then back to the lower vertex results in said ber allowing apredetermined degree of periodic barrel cam being rotated at least threetimes in sucovertravel of said rotatable drive means relative tocessively opposite directions. said rotatable support member during eachindex- 4. A multi-directional indexing drive mechanism in ing period,said periodic overtravel allowing the accordance with claim 2 furthercomprising: support member to be selectively stopped at differaspring-biased pivotal lever positioned relative to ent predeterminedangular positions relative to said rotatable drive-means, and with therotation of said support member and the vertical displacement thereofbeing produced in a sequential manner.

said orbital cam passageway so as to normally close the lower vertexentrance to one section thereof while said cam follower, secured to saidreciprocal 9. A multi-directional indexing'drive mechanism for use witha rotary indexing table, comprising:

rotatable drive means including a barrel cam having a passageway formedtherein, said passageway havovertravel of said rotatable drive meansrelative to said support member during each indexing period, saidperiodic overtravel allowing the rotatable support member to beselectively stopped at different predetermined angular positionsrelative to said rotatable drive means, and with the rotation of saidsupport member and the vertical displacement ing a first section whichis non-linear along at least thereof being produced in a sequentialmanner by a portion of the length thereof, the terminating saidrotatable and reciprocal drive means. ends of said first section beingspaced apart and 12. A multi-directional indexing drive mechanism inaligned at least generally in an axial direction of accordance withclaim 11 further comprising: said barrel cam, and said passageway havinga secbiasing means associated with said rotatable drive end sectionmerging at opposite ends at inclined means for imparting a supplementalrotational angles with the corresponding ends of said first secforcethereto each time said cam follower passes tion so as to form acontinuous orbital passageway through the upper communicating vertex ofsaid with upper and lower communicating vertices in orbital passagewayin a predetermined direction. the wall of said barrel cam, saidrotatable drive 13. A multi-directional indexing apparatus comprismeansfurther including rotatable support means to 15 ing: independently holdthe wall portion of said barrel a rotary indexing table including acylindrical support cam defined within said orbital passageway infreemember secured thereto and oriented axially space relationship withrespect to the remaining thereof; wall area of said barrel cam, androtatable drive means coupled to said table through reciprocal drivemeans including a cylindrical drive said support member and including atleast one cyrod at least partially extending within and movablelindrical cam member having a continuous orbital relative to said barrelcam, said drive rod having a cam passageway formed in the wall thereof,said cam follower rotatably secured thereto and concam passageway beingoriented generally in the fined within said passageway, said camfollower axial direction of said cylindrical cam member and beingmovable along a rectilinear path at least bebeing formed by two mergingsections into a contween said lower and upper vertices, said camfoltinuous orbital passageway with upper and lower lower in moving alongsaid rectilinear path thereby communicating vertices, with at least onesection forcing said barrel'cam to be variably rotationally .ofthepassagcway being non-linear; and displaced and in oppositedirections, the degree of reciprocal drive means at least partiallyextending rotation and the direction thereof being dependent within andmovable relative to said cylindrical cam upon both the degree oflongitudinal displacement member of said rotatable drive means, saidreciproand the angle of inclination of said passageway at ca] drivemeans having a rotatable cam follower seany point therealong relative tothe rectilinear path cured thereto and communicating with said cam oftravel of said cam follower, as measured from an passageway, said camfollower during each indexarbitrary neutral position of said barrel cam.ing period being reciprocally movable along said 10. A multidirectionalindexing drive mechanism in passageway, with movement confined along arectiaccordance with claim 9 further comprising: linear path so as torotate at least said cylindrical a linear passageway communicating withsaid lower cam member whenever the cam follower commuvertex of saidorbital passageway and defining nicates with said non-linear section ofsaid passagewhenever said cam follower is confined therein a 40 way, theparticular direction and magnitude of roneutral position and a dwellperiod of said rotatable tation imparted to said cylindrical cam memberdrive means; being dependent upon both the degree oflongitudispring-biased pivotal lever positioned relative to naldisplacement and the angle of inclination of said orbital cam passagewayso as to normally close said non-linear section of the passageway at anythe lower vertex entrance to one section thereof point therealongrelative to the rectilinear path of while said cam follower, -secured tosaid drive travel of said cam follower, as measured from an means, movesupwardly along the other section arbitrary neutral position of saidcylindrical cam thereof, said lever being spring-biased to an openmember, and wherein said cam follower, in moving position by said camfollower when the latter so through successive complete orbits in saidorbital makes contact therewith in moving downwardly cam passageway,causes said cylindrical cam memalong the initially closed section ofsaid passageher to be rotated in opposite directions out of, and way,and back into, its arbitrary neutral position on each a spring-biasedrotatable indextable support member orbit in the same predeterminedsequence.

coupled to said drive means. 14. A multi-directional indexing apparatuscomprisll. A multi-directional indexing drive mechanism in ing: aaccordance with claim 10 further comprising: I a rotary indexing tableincluding acylindrical support vertical displacement means secured tosaid rotatable member secured thereto and oriented axially drive meansand cooperating with said rotatable thereof; support member toperiodically vertically displace rotatable drive means coupled to saidtable through the last-mentioned member a predetermined dissaid supportmember and including a cylindrical tance upon being rotated to specificangular posibarrel cam having a cam passageway formed in the lionsduring each indexing period, and I wall thereof, said cam passagewaybeing oriented stop means coupled to said rotatable support memgenerallyin the axialdirection of said barrel cam ber allowing a predetermineddegree of periodic and being formed by two merging sections into acontinuous orbital passageway with upper and lower communicatingvertices, with at least one section of the passageway being non-linear,said cylindrical support member of said indexing table being supportedon said rotatable drive means and being spring-biased with respectthereto in a direction axially of said support member; and reciprocaldrive means including a cylindrical drive rod at least partiallyextending within and movable relative to said cylindrical barrel cam ofsaid rotatable drive means, said drive rod having a rotatable camfollower secured thereto and communicating with said cam passageway,said cam follower during each indexing period being reciprocally movablealong said' passageway, with movement confined along a rectilinear pathso as to rotate'at least said barrel cam whenever the cam followercommunicates with said non-linear section of said passageway, theparticular direction and magnitude of rotation imparted to said barrelcam being dependent upon both the degree of longitudinal displacementand the angle of inclination of said non-linear section of thepassageway at any point therealong relative to'the rectilinear path oftravel of said cam follower, as measured from an arbitrary neutralposition of said barrel cam.

15. A multi-directional indexing apparatus in accordance with claim 14further comprising:

a spring-biased pivotal lever positioned relative to said orbital campassageway so as to normally close the lower vertex entrance to oneorbital section thereof while said cam follower, secured to saidreciprocal drive means, moves upwardly along the other section thereof,said lever being springbiased to an open position by said cam followerwhenever the latter makes contact therewith in moving downwardly alongthe initially closed section of said passageway;

vertical displacement means secured to said rotatable drive menas andcooperating with said index table support member to periodicallyvertically displace the last-mentioned member and the index tableassociated therewith a predetermined distance upon being rotated tospecific angular positions during each indexing period.

16. A multi-directional indexing apparatus in accordance with claim 15wherein said index table is formed with a plurality of outwardlyextending and circumferentially spaced fingers, each supporting anarticle carrying fixture, and said indexing apparatus furthercomprising:

stop means coupled to said index table support member allowing apredetermined degree of periodic overtravel of said rotatable drivemeans relative to said support member during each indexing period, saidperiodic overtravel allowing the support member and the index tableassociated therewith to be selectively stopped at difi'erentpredetermined angular positions relative to said rotatable drive means,and with the rotation of said support member and the verticaldisplacement thereof being produced in a sequential manner by theinterrelated movements of said rotatable and reciprocal drive means.

17. A multi-directional indexing apparatus comprisa rotary indexingtable including a cylindrical support member secured thereto andextending axially therethrough;

stationary table support means;

a cylindrical stationary housing supported by said support table; 1

rotatable drive means mounted within said cylindrical housing andextending upwardly at least in part through an oversized aperture insaid table support means, said rotatable drive means being coupled tosaid index table through said associated support member and including acylindrical barrel cam having a cam passageway formed in the wallthereof, said passageway having a first section which is arcuate alongat least a portion of the length thereof, said first portion beingoriented generally in the axial direction of said barrel cam,

and a second section merging at opposite ends and a at oppositelyinclined angles with the corresponding ends of said first section so asto form a continuous orbital passageway with upper and lowercommunicating vertices, and

reciprocal drive means at least partially extending within and movableaxially relative to said barrel cam, said reciprocal drive means havinga rotatable cam follower secured thereto and communicating with said campassageway, said cam follower during each indexing period beingrectilinearly movable at least from a first position coinciding with thelower vertex of said passageway to a second position coinciding withsaid upper vertex of said passageway and then back to said firstposition, said rectilinear movement of said cam follower during eachindexing period resulting in at least said barrel cam being rotated atleast once in opposite directions, the particular direction andmagnitude of rotation imparted to said barrel cam being dependent uponboth the degree of longitudinal displacement and the angle ofinclination of said orbital passageway at any point therealong relativeto the rectilinear path of travel of said cam follower, as measured froman arbitrary neutral position of said barrel cam.

18. A multi-directional indexing apparatus in accordance with claim 17further comprising:

a linear passageway communicating with said lower vertex of said orbitalpassageway and defining whenever said cam follower is confined therein aneutral position and a dwell period of at least said barrel cam, and

a spring-biased pivotal lever positioned relative to said orbital campassageway so as to normally close the lower vertex entrance to onesection thereof while said cam follower, secured to said reciprocaldrive means, moves upwardly along the other section thereof, said leverbeing spring-biased to an open position by said cam follower wheneverthe latter makes contact therewith in moving downwardly along theinitially closed section of said passageway.

19. A multi-directional indexing apparatus in in accordance with claim18 further comprising:

vertical displacement means secured to said rotatable drive means andcooperating with said cylindrical support member to periodicallyvertically displace the last-mentioned member and the associated indextable a predetermined distance upon being rotated to specific angularpositions during each indexing period, and

stop means coupled to said cylindrical support member allowing apredetermined degree of periodic overtravel of said rotatable drivemeans relative to said support member and associated index table duringeach indexing period, said periodic overtravel allowing the supportmember to be selectively stopped at different predetermined angularpositions relative to said rotatable drive means, and with the rotationof said support member and the vertical displacement thereof beingproduced in a sequential manner by the cooperative movements of saidrotatable and reciprocal drive means.

20. A multi-directional indexing apparatus in accordance with claim 18wherein said index table is formed with a plurality of outwardlyextending and circumferentially spaced article carrying fingers, witheach finger supporting an article holding fixture, and furthercomprising:

biasing means associated with said rotatable drive to selectivelydeposit articles on and pick up articles from the respectively alignedstationary work fixtures.

22. A multi-directional indexing apparatus in accordance with claim 21further comprising:

means for imparting a supplemental rotational force thereto in adirection which assists said cam follower in passing through the uppercommunicating vertex of said orbital passageway.

21. A multi-directional indexing apparatus in accordance with claim l9wherein said index table is formed with a plurality of outwardlyextending and circumferentially spaced fingers, each supporting anarticle carrying fixture, and said indexing apparatus furthercomprising:

a plurality of stationary work fixtures supported'on said stationarytable support means and circumferentially disposed beneath said indextable so as to allow respective alignment of said stationary workfixtures with said index table fingers during each indexing period, andwherein the movement of said cam follower from said lower vertex to theupper vertex and back to the lower vertex of said orbital passagewayresults in said index table fingers being rotated at least from a dwellposition, whereat said respective fingers are interposed betweendifferent pairs of adjacent stationary work fixtures to a position, uponbeing rotated in one direction, whereat at least certain of saidrespective fingers are aligned with different stationary work fixtures,comprising retractable work performing operating heads disposed abovesaid index table and respectively positioned in alignment with at leastcertain of said stationary work fixtures, said operating heads beingactuated in a sequential manner with respect to the rotational andvertical displacements imparted to said index table so as to movedownwardly through the spaces defined between adjacent fingers of saidindexing table while the latter is in the dwell position.

23. A multi-directional indexing drive mechanism for use with a rotaryindexing table, comprising:

rotatable drive means including a cylindrical barrel cam having a campassageway formed in the wall thereof and oriented generally in theaxial direction of said barrel cam, said cam passageway having a firstsection which is arcuate along at least a portion of the length thereofand having a second section merging at opposite ends with differentspaced regions of said first section in such a manner as to form acontinuous orbital passageway with upper and lower communicatingvertices in said barrel cam; and

reciprocal drive means including a cylindrical drive rod atleastpartially extending within and movable relative to said cylindricalbarrel cam of said rotatable drive means, said cylindrical drive rodhaving a rotatable cam follower secured thereto and communicating withsaid cam passageway, said cam follower during each indexing period beingreciprocally movable along said passageway, with movement confined alonga rectilinear path so as to rotate at least said barrel vcarnwheneverthe cam follower communicates with the arcuate first section of saidbarrel cam, the particular direction and magnitude of rotation impartedto said barrel cam being dependent upon both the degree of longitudinaldisplacement andthe'angle of inclination of said arcuate first sectionof the passageway at any point therealong relative to the rectilinearpath of travelof said cam follower, as measured from an arbitraryneutral position of said barrel cam, and wherein said cam follower inmoving from said lower vertex of said orbital passageway to the uppervertex thereof and then back to the lower vertex results in said barrelcam being rotated in opposite directions during each indexing period.

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1. A multi-directional indexing drive mechanism for use with a rotaryindexing table, comprising: rotatable drive means including at least onecylindrical member having a continuous orbital cam passageway formed inthe wall thereof and oriented generally in the axial direction of saidcylindrical member, said cam passageway having a first section which isnon-linear along at least a portion of its length, and having a secondsection which merges at opposite ends with said first section to form acontinuous orbital passageway with upper and lower communicatingvertices; and reciprocal drive means at least partially extending withinand movable relative to said cylindrical member of said rotatable drivemeans, said reciprocal drive means having a rotatable cam followersecured thereto and communicating with said cam passageway, said camfollower during each indexing period being reciprocally movable alongsaid passageway, with movement confined along a rectilinear path so asto rotate at least said cylindrical cam member whenever the cam followercommunicates with said non-linear section of said passageway, theparticular direction and magnitude of rotation imparted to saidcylindrical cam member being dependent upon both the degree oflongitudinal displacement and the angle of inclination of saidnon-linear section of the passageway at any point therealong relative tothe rectilinear path of travel of said cam follower, as measured from anarbitrary neutral position of said cylindrical cam member, and whereinsaid cam follower, in moving through successive complete orbits in saidorbital cam passageway, causes said cylindrical cam member to be rotatedin opposite directions out of, and back into, its arbitrary neutralposition on each orbit in the same predetermined sequence.
 2. Amulti-directional indexing drive mechanism for use with a rotary indextable, comprising: rotatable drive means including a cylindrical memberhaving a cam passageway formed in the wall thereof, said passagewayhaving a first section which is arcuate along at least a portion of thelength thereof, said first portion being oriented generally in the axialdirection of said cylindrical member, and a second section merging atopposite ends and at oppositely inclined angles with the correspondingends of said first section so as to form a continuous orbital passagewaywith upper and lower communicating vertices, and reciprocal drive meansat least partially extending within and movable axially relative to saidcylindrical cam member, said reciprocal drive means having a rotatablecam follower secured thereto and communicating with said cam passageway,said cam follower during each indexing period being rectilinearlymovable at least from a first position coinciding with the lower vertexof said passageway to a second position coinciding with said uppervertex of said passageway and then back to said first position, saidrectilinear movement of said cam follower during each indexing periodresulting in at least said cylindrical cam member being rotated at leastonce in opposite directions, the particular direction and magnitude ofrotation imparted to said cylindrical cam member being dependent uponboth the degree of longitudinal displacement and the angle ofinclination of said orbital passageway at any point therealong relativeto the rectilinear path of travel of said cam follower, as measured froman arbitrary neutral position of said cylindrical cam member.
 3. Amulti-directional indexing drive mechanism in accordance with claim 2further comprising: a third linear passageway communicating with saidlower vertex of said orbital passageway and defining whenever said camfollower is confined therein a neutral position and a dwell period ofsaid rotatable drive means, and wherein said cylindrical membercomprises a baRrel cam, wherein said reciprocal drive means includes acylindrical drive rod, wherein said second section of said passagewayincludes an arcuate portion, and wherein said cam follower in movingfrom said lower vertex of said orbital passageway to the upper vertexthereof and then back to the lower vertex results in said barrel cambeing rotated at least three times in successively opposite directions.4. A multi-directional indexing drive mechanism in accordance with claim2 further comprising: a spring-biased pivotal lever positioned relativeto said orbital cam passageway so as to normally close the lower vertexentrance to one section thereof while said cam follower, secured to saidreciprocal drive means, moves upwardly along the other section thereof,said lever being spring-biased to an open position by said cam followerwhenever the latter makes contact therewith in moving downwardly alongthe initially closed section of said passageway.
 5. A multi-directionalindexing drive mechanism in accordance with claim 2 further comprising:a spring-biased rotatable index table support member coupled to saidrotatable drive means, and vertical displacement means secured to saidrotatable drive means and cooperating with said support member toperiodically vertically displace the last-mentioned member apredetermined distance upon being rotated to specific angular positionsduring each indexing period.
 6. A multi-directional indexing drivemechanism in accordance with claim 5 further comprising: stop meanscoupled to said rotatable support member allowing a predetermined degreeof periodic overtravel of said rotatable drive means relative to saidsupport member during each indexing period, said periodic overtravelallowing the rotatable support member to be selectively displaced bydifferent angular degrees of rotation than said rotatable drive meansduring each indexing period.
 7. A multi-directional indexing drivemechanism in accordance with claim 3 further comprising: a spring-biasedrotatable index table support member coupled to said rotatable drivemeans, vertical displacement means secured to said rotatable drive meansand cooperating with said support member to periodically verticallydisplace the support member a predetermined distance upon being rotatedto specific angular positions during each indexing period, and stopmeans coupled to said rotatable support member allowing a predetermineddegree of periodic overtravel of said rotatable drive means relative tosaid rotatable support member during each indexing period, said periodicovertravel allowing the support member to be selectively stopped atdifferent predetermined angular positions relative to said rotatabledrive means, and with the rotation of said support member and thevertical displacement thereof being produced in a sequential manner bysaid rotatable and reciprocal drive means.
 8. A multi-directionalindexing drive mechanism in accordance with claim 4 further comprising:a spring-biased rotatable index table support member coupled to saidrotatable drive means, vertical displacement means secured to saidrotatable drive means and cooperating with said support member toperiodically vertically displace the support member a predetermineddistance upon being rotated to specific angular positions during eachindexing period, and stop means coupled to said rotatable support memberallowing a predetermined degree of periodic overtravel of said rotatabledrive means relative to said rotatable support member during eachindexing period, said periodic overtravel allowing the support member tobe selectively stopped at different predetermined angular positionsrelative to said rotatable drive means, and with the rotation of saidsupport member and the vertical displacement thereof being produced in asequential manner.
 9. A multi-directional indexing drive mechanism foruse with a rotary indexing table, comprising: rotatable drive Meansincluding a barrel cam having a passageway formed therein, saidpassageway having a first section which is non-linear along at least aportion of the length thereof, the terminating ends of said firstsection being spaced apart and aligned at least generally in an axialdirection of said barrel cam, and said passageway having a secondsection merging at opposite ends at inclined angles with thecorresponding ends of said first section so as to form a continuousorbital passageway with upper and lower communicating vertices in thewall of said barrel cam, said rotatable drive means further includingrotatable support means to independently hold the wall portion of saidbarrel cam defined within said orbital passageway in free-spacerelationship with respect to the remaining wall area of said barrel cam,and reciprocal drive means including a cylindrical drive rod at leastpartially extending within and movable relative to said barrel cam, saiddrive rod having a cam follower rotatably secured thereto and confinedwithin said passageway, said cam follower being movable along arectilinear path at least between said lower and upper vertices, saidcam follower in moving along said rectilinear path thereby forcing saidbarrel cam to be variably rotationally displaced and in oppositedirections, the degree of rotation and the direction thereof beingdependent upon both the degree of longitudinal displacement and theangle of inclination of said passageway at any point therealong relativeto the rectilinear path of travel of said cam follower, as measured froman arbitrary neutral position of said barrel cam.
 10. Amulti-directional indexing drive mechanism in accordance with claim 9further comprising: a linear passageway communicating with said lowervertex of said orbital passageway and defining whenever said camfollower is confined therein a neutral position and a dwell period ofsaid rotatable drive means; a spring-biased pivotal lever positionedrelative to said orbital cam passageway so as to normally close thelower vertex entrance to one section thereof while said cam follower,secured to said drive means, moves upwardly along the other sectionthereof, said lever being spring-biased to an open position by said camfollower when the latter makes contact therewith in moving downwardlyalong the initially closed section of said passageway, and aspring-biased rotatable index table support member coupled to said drivemeans.
 11. A multi-directional indexing drive mechanism in accordancewith claim 10 further comprising: vertical displacement means secured tosaid rotatable drive means and cooperating with said rotatable supportmember to periodically vertically displace the last-mentioned member apredetermined distance upon being rotated to specific angular positionsduring each indexing period, and stop means coupled to said rotatablesupport member allowing a predetermined degree of periodic overtravel ofsaid rotatable drive means relative to said support member during eachindexing period, said periodic overtravel allowing the rotatable supportmember to be selectively stopped at different predetermined angularpositions relative to said rotatable drive means, and with the rotationof said support member and the vertical displacement thereof beingproduced in a sequential manner by said rotatable and reciprocal drivemeans.
 12. A multi-directional indexing drive mechanism in accordancewith claim 11 further comprising: biasing means associated with saidrotatable drive means for imparting a supplemental rotational forcethereto each time said cam follower passes through the uppercommunicating vertex of said orbital passageway in a predetermineddirection.
 13. A multi-directional indexing apparatus comprising: arotary indexing table including a cylindrical support member securedthereto and oriented axially thereof; rotatable drive means coupled tosaid table through said support member and including at leaSt onecylindrical cam member having a continuous orbital cam passageway formedin the wall thereof, said cam passageway being oriented generally in theaxial direction of said cylindrical cam member and being formed by twomerging sections into a continuous orbital passageway with upper andlower communicating vertices, with at least one section of thepassageway being non-linear; and reciprocal drive means at leastpartially extending within and movable relative to said cylindrical cammember of said rotatable drive means, said reciprocal drive means havinga rotatable cam follower secured thereto and communicating with said campassageway, said cam follower during each indexing period beingreciprocally movable along said passageway, with movement confined alonga rectilinear path so as to rotate at least said cylindrical cam memberwhenever the cam follower communicates with said non-linear section ofsaid passageway, the particular direction and magnitude of rotationimparted to said cylindrical cam member being dependent upon both thedegree of longitudinal displacement and the angle of inclination of saidnon-linear section of the passageway at any point therealong relative tothe rectilinear path of travel of said cam follower, as measured from anarbitrary neutral position of said cylindrical cam member, and whereinsaid cam follower, in moving through successive complete orbits in saidorbital cam passageway, causes said cylindrical cam member to be rotatedin opposite directions out of, and back into, its arbitrary neutralposition on each orbit in the same predetermined sequence.
 14. Amulti-directional indexing apparatus comprising: a rotary indexing tableincluding a cylindrical support member secured thereto and orientedaxially thereof; rotatable drive means coupled to said table throughsaid support member and including a cylindrical barrel cam having a campassageway formed in the wall thereof, said cam passageway beingoriented generally in the axial direction of said barrel cam and beingformed by two merging sections into a continuous orbital passageway withupper and lower communicating vertices, with at least one section of thepassageway being non-linear, said cylindrical support member of saidindexing table being supported on said rotatable drive means and beingspring-biased with respect thereto in a direction axially of saidsupport member; and reciprocal drive means including a cylindrical driverod at least partially extending within and movable relative to saidcylindrical barrel cam of said rotatable drive means, said drive rodhaving a rotatable cam follower secured thereto and communicating withsaid cam passageway, said cam follower during each indexing period beingreciprocally movable along said passageway, with movement confined alonga rectilinear path so as to rotate at least said barrel cam whenever thecam follower communicates with said non-linear section of saidpassageway, the particular direction and magnitude of rotation impartedto said barrel cam being dependent upon both the degree of longitudinaldisplacement and the angle of inclination of said non-linear section ofthe passageway at any point therealong relative to the rectilinear pathof travel of said cam follower, as measured from an arbitrary neutralposition of said barrel cam.
 15. A multi-directional indexing apparatusin accordance with claim 14 further comprising: a spring-biased pivotallever positioned relative to said orbital cam passageway so as tonormally close the lower vertex entrance to one orbital section thereofwhile said cam follower, secured to said reciprocal drive means, movesupwardly along the other section thereof, said lever being spring-biasedto an open position by said cam follower whenever the latter makescontact therewith in moving downwardly along the initially closedsection of said passageway; vertical displacement means secured to saidrotatable drive menas and cooperating with said index table supportmembEr to periodically vertically displace the last-mentioned member andthe index table associated therewith a predetermined distance upon beingrotated to specific angular positions during each indexing period.
 16. Amulti-directional indexing apparatus in accordance with claim 15 whereinsaid index table is formed with a plurality of outwardly extending andcircumferentially spaced fingers, each supporting an article carryingfixture, and said indexing apparatus further comprising: stop meanscoupled to said index table support member allowing a predetermineddegree of periodic overtravel of said rotatable drive means relative tosaid support member during each indexing period, said periodicovertravel allowing the support member and the index table associatedtherewith to be selectively stopped at different predetermined angularpositions relative to said rotatable drive means, and with the rotationof said support member and the vertical displacement thereof beingproduced in a sequential manner by the interrelated movements of saidrotatable and reciprocal drive means.
 17. A multi-directional indexingapparatus comprising: a rotary indexing table including a cylindricalsupport member secured thereto and extending axially therethrough;stationary table support means; a cylindrical stationary housingsupported by said support table; rotatable drive means mounted withinsaid cylindrical housing and extending upwardly at least in part throughan oversized aperture in said table support means, said rotatable drivemeans being coupled to said index table through said associated supportmember and including a cylindrical barrel cam having a cam passagewayformed in the wall thereof, said passageway having a first section whichis arcuate along at least a portion of the length thereof, said firstportion being oriented generally in the axial direction of said barrelcam, and a second section merging at opposite ends and at oppositelyinclined angles with the corresponding ends of said first section so asto form a continuous orbital passageway with upper and lowercommunicating vertices, and reciprocal drive means at least partiallyextending within and movable axially relative to said barrel cam, saidreciprocal drive means having a rotatable cam follower secured theretoand communicating with said cam passageway, said cam follower duringeach indexing period being rectilinearly movable at least from a firstposition coinciding with the lower vertex of said passageway to a secondposition coinciding with said upper vertex of said passageway and thenback to said first position, said rectilinear movement of said camfollower during each indexing period resulting in at least said barrelcam being rotated at least once in opposite directions, the particulardirection and magnitude of rotation imparted to said barrel cam beingdependent upon both the degree of longitudinal displacement and theangle of inclination of said orbital passageway at any point therealongrelative to the rectilinear path of travel of said cam follower, asmeasured from an arbitrary neutral position of said barrel cam.
 18. Amulti-directional indexing apparatus in accordance with claim 17 furthercomprising: a linear passageway communicating with said lower vertex ofsaid orbital passageway and defining whenever said cam follower isconfined therein a neutral position and a dwell period of at least saidbarrel cam, and a spring-biased pivotal lever positioned relative tosaid orbital cam passageway so as to normally close the lower vertexentrance to one section thereof while said cam follower, secured to saidreciprocal drive means, moves upwardly along the other section thereof,said lever being spring-biased to an open position by said cam followerwhenever the latter makes contact therewith in moving downwardly alongthe initially closed section of said passageway.
 19. A multi-directionalindexing apparatus in in accordance with claim 18 further Comprising:vertical displacement means secured to said rotatable drive means andcooperating with said cylindrical support member to periodicallyvertically displace the last-mentioned member and the associated indextable a predetermined distance upon being rotated to specific angularpositions during each indexing period, and stop means coupled to saidcylindrical support member allowing a predetermined degree of periodicovertravel of said rotatable drive means relative to said support memberand associated index table during each indexing period, said periodicovertravel allowing the support member to be selectively stopped atdifferent predetermined angular positions relative to said rotatabledrive means, and with the rotation of said support member and thevertical displacement thereof being produced in a sequential manner bythe cooperative movements of said rotatable and reciprocal drive means.20. A multi-directional indexing apparatus in accordance with claim 18wherein said index table is formed with a plurality of outwardlyextending and circumferentially spaced article carrying fingers, witheach finger supporting an article holding fixture, and furthercomprising: biasing means associated with said rotatable drive means forimparting a supplemental rotational force thereto in a direction whichassists said cam follower in passing through the upper communicatingvertex of said orbital passageway.
 21. A multi-directional indexingapparatus in accordance with claim 19 wherein said index table is formedwith a plurality of outwardly extending and circumferentially spacedfingers, each supporting an article carrying fixture, and said indexingapparatus further comprising: a plurality of stationary work fixturessupported on said stationary table support means and circumferentiallydisposed beneath said index table so as to allow respective alignment ofsaid stationary work fixtures with said index table fingers during eachindexing period, and wherein the movement of said cam follower from saidlower vertex to the upper vertex and back to the lower vertex of saidorbital passageway results in said index table fingers being rotated atleast from a dwell position, whereat said respective fingers areinterposed between different pairs of adjacent stationary work fixturesto a position, upon being rotated in one direction, whereat at leastcertain of said respective fingers are aligned with different stationarywork fixtures, comprising one set thereof, and then, upon said fingersbeing rotated in the opposite direction, having at least certain of saidfingers respectively aligned with different stationary work fixtures,comprising a second set thereof, before said fingers are rotated back tothe initial dwell position, said index table being vertically displaceddownwardly by said vertical displacement means each time at leastcertain of the respective index fingers are positioned in alignment withdifferent stationary work fixtures so that said article carryingfixtures may be actuated to selectively deposit articles on and pick uparticles from the respectively aligned stationary work fixtures.
 22. Amulti-directional indexing apparatus in accordance with claim 21 furthercomprising: retractable work performing operating heads disposed abovesaid index table and respectively positioned in alignment with at leastcertain of said stationary work fixtures, said operating heads beingactuated in a sequential manner with respect to the rotational andvertical displacements imparted to said index table so as to movedownwardly through the spaces defined between adjacent fingers of saidindexing table while the latter is in the dwell position.
 23. Amulti-directional indexing drive mechanism for use with a rotaryindexing table, comprising: rotatable drive means including acylindrical barrel cam having a cam passageway formed in the wallthereof and oriented generally in the axial direction of said barrelcam, said cam passageway having a first section which is arcuate alongat least a portion of the length thereof and having a second sectionmerging at opposite ends with different spaced regions of said firstsection in such a manner as to form a continuous orbital passageway withupper and lower communicating vertices in said barrel cam; andreciprocal drive means including a cylindrical drive rod at leastpartially extending within and movable relative to said cylindricalbarrel cam of said rotatable drive means, said cylindrical drive rodhaving a rotatable cam follower secured thereto and communicating withsaid cam passageway, said cam follower during each indexing period beingreciprocally movable along said passageway, with movement confined alonga rectilinear path so as to rotate at least said barrel cam whenever thecam follower communicates with the arcuate first section of said barrelcam, the particular direction and magnitude of rotation imparted to saidbarrel cam being dependent upon both the degree of longitudinaldisplacement and the angle of inclination of said arcuate first sectionof the passageway at any point therealong relative to the rectilinearpath of travel of said cam follower, as measured from an arbitraryneutral position of said barrel cam, and wherein said cam follower inmoving from said lower vertex of said orbital passageway to the uppervertex thereof and then back to the lower vertex results in said barrelcam being rotated in opposite directions during each indexing period.